US6332447B1 - Diesel engine - Google Patents

Diesel engine Download PDF

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Publication number
US6332447B1
US6332447B1 US09/591,425 US59142500A US6332447B1 US 6332447 B1 US6332447 B1 US 6332447B1 US 59142500 A US59142500 A US 59142500A US 6332447 B1 US6332447 B1 US 6332447B1
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Prior art keywords
engine
intake air
running state
air amount
fuel
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Expired - Fee Related
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US09/591,425
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English (en)
Inventor
Shuji Kimura
Osamu Aoki
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Nissan Motor Co Ltd
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Nissan Motor Co Ltd
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Assigned to NISSAN MOTOR CO., LTD. reassignment NISSAN MOTOR CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AOKI, OSAMU, KIMURA, SHUJI
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
    • F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
    • F02B23/0696—W-piston bowl, i.e. the combustion space having a central projection pointing towards the cylinder head and the surrounding wall being inclined towards the cylinder wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D33/00—Controlling delivery of fuel or combustion-air, not otherwise provided for
    • F02D33/02—Controlling delivery of fuel or combustion-air, not otherwise provided for of combustion-air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/04—Introducing corrections for particular operating conditions
    • F02D41/08—Introducing corrections for particular operating conditions for idling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
    • F02D41/402—Multiple injections
    • F02D41/403—Multiple injections with pilot injections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F02F3/26—Pistons  having combustion chamber in piston head
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/14—Direct injection into combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
    • F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
    • F02B23/0618—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston having in-cylinder means to influence the charge motion
    • F02B23/0621—Squish flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
    • F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
    • F02B23/0672—Omega-piston bowl, i.e. the combustion space having a central projection pointing towards the cylinder head and the surrounding wall being inclined towards the cylinder center axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0223—Variable control of the intake valves only
    • F02D13/0234—Variable control of the intake valves only changing the valve timing only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0002—Controlling intake air
    • F02D2041/001—Controlling intake air for engines with variable valve actuation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0002—Controlling intake air
    • F02D2041/0022—Controlling intake air for diesel engines by throttle control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D41/0047—Controlling exhaust gas recirculation [EGR]
    • F02D41/005—Controlling exhaust gas recirculation [EGR] according to engine operating conditions
    • F02D41/0057—Specific combustion modes
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/40—Engine management systems

Definitions

  • This invention relates to a diesel engine which reduces noise and vibration, and especially during idle running of an engine.
  • the maximum internal cylinder pressure (i.e., the maximum generated pressure in a cylinder) is at a very high level, the maximum internal cylinder pressure, particularly in the idle state, is far higher than in a gasoline engine with a throttle in an intake system (“Isuzu Technical Papers”, Vol. 99, p. 85).
  • a technique for reducing noise in the idle running state of a diesel engine is disclosed in Japanese Patent Publication Tokkai Sho 56-101031.
  • a shutter is provided in an intake air passage of the engine, this shutter being closed in the idle running state. This reduces the intake air amount and decreases the pressure in the compression stroke. By decreasing the compression pressure, the maximum pressure generated when fuel is burnt also decreases, so noise in the idle running state is therefore mitigated.
  • the present invention provides a diesel engine which comprises a piston having a dish-shaped combustion chamber is formed on its top surface, a fuel injector situated coaxially with the combustion chamber which injects fuel directly into a cylinder, an intake air amount control device which varies an intake air amount aspirated by the engine, and a detector which detects a running state of the engine.
  • the diesel engine further comprises a mechanism for determining whether or not the engine is an idle running state or a normal running state, a mechanism for controlling the intake air amount controller based on the engine running state so that the intake air amount in the idle running state is less than the intake air amount in the normal running state, and a mechanism for controlling the fuel injector so that part of the fuel is injected before a main injection when the engine is in the idle running state.
  • FIG. 1 is a schematic block diagram showing an embodiment of this invention.
  • FIG. 2 is a cross-sectional view of an engine according to this embodiment.
  • FIG. 3 is a cross-sectional view of a piston according to this embodiment.
  • FIG. 4 is a flowchart showing the control performed according to this embodiment.
  • FIG. 5 is a descriptive diagram showing how an internal cylinder pressure varies according to this embodiment.
  • FIG. 6 is a descriptive diagram showing relations between the internal cylinder pressure, unburnt HC (Hydrocarbon) and combustion noise.
  • FIG. 7 is a cross-sectional view of a variable valve mechanism according to another embodiment of this invention.
  • FIG. 8 is a descriptive diagram showing an open/close timing of an intake air valve.
  • FIG. 9 is a descriptive diagram showing how the internal cylinder pressure varies.
  • FIG. 10 is a descriptive diagram showing a fuel pilot injection timing.
  • FIG. 11 is a cross-sectional view of a piston for purposes of comparison with the present invention.
  • FIG. 1 is a schematic diagram of a diesel engine to which this invention is applied.
  • a throttle valve 3 is provided in an intake air passage 2 connected to an engine body 1 .
  • the throttle valve 3 is driven by an actuator 6 so that its opening varies, and the air amount aspirated by the engine is thereby regulated.
  • the actuator 6 varies the opening of the throttle valve 3 according to a control signal from a controller 20 .
  • the engine comprises a turbocharger, and due to the rotation force of an exhaust gas turbine 5 disposed in an exhaust gas passage 4 , a compressor, not shown, is rotation driven to supercharge the air delivered to the intake air passage 2 .
  • An exhaust gas recirculation passage 7 connects the intake air passage 2 with the exhaust gas passage 4 , part of the exhaust gas passing through this exhaust gas recirculation passage being recirculated to the intake air passage 2 .
  • a control valve 8 which regulates the amount of recirculated exhaust gas according to running conditions is disposed in the exhaust gas recirculation passage 7 .
  • the valve opening of the control valve 8 varies according to a negative pressure supplied by a negative pressure regulating valve 9 .
  • the negative pressure regulating valve 9 operates according to a negative pressure control signal from the controller 20 , regulates the negative pressure from a vacuum pump, not shown, and supplies this regulated negative pressure to the control valve 8 .
  • a cooler 10 is disposed downstream of the control valve 8 .
  • This cooler 10 uses the cooling water for cooling the engine body 1 to cool the exhaust gas flowing through the exhaust gas recirculation passage 7 .
  • Signals detected by an engine rotation speed sensor 24 , accelerator opening sensor 25 , cooling water temperature sensor 26 and intake air temperature sensor 27 are input to the controller 20 .
  • FIG. 2 is a detailed drawing of the engine body 1 .
  • An injector 16 for injecting fuel into a cylinder 12 is installed in a cylinder head 11 .
  • the injector 16 is disposed effectively immediately above a center axis A of the combustion chamber 14 , and high-pressure fuel is supplied by the injector 16 via a high-pressure pipe 17 connected to each cylinder.
  • the injector 16 comprises a built-in solenoid valve, this solenoid valve is operating in response to a fuel injection signal from the controller 20 to inject fuel.
  • the injection timing and injection amount of the fuel injected by the injector 16 can be freely controlled by varying the fuel injection signal from the controller 20 .
  • the injector 16 is so designed that the fuel injection rate (fuel injection amount per unit time) is larger than in an ordinary injector and the fuel injection period in the normal running state is as short as possible.
  • the high pressure pipe 17 provided to each cylinder is connected to a common rail 18 which has a fixed capacity and is common to all cylinders.
  • High-pressure fuel is supplied from a fuel pump 21 to the common rail 18 via a high pressure pipe 19 .
  • the discharge pressure of the fuel pump 21 is controlled by the controller 20 , and the fuel pressure in the common rail 18 coincides with a target pressure determined according to the running conditions.
  • An intake air valve 22 is opened and closed by a cam, not shown, in synchronism with the engine rotation, and connects or disconnects the intake air passage 2 with a combustion space 15 in the cylinder.
  • an exhaust gas valve 23 is opened and closed in synchronism with the engine rotation, and connects or disconnects the exhaust gas passage 4 with the combustion space 15 in the cylinder.
  • the compression ratio of this engine is set to 14 . In other words, this is a very low compression ratio for a diesel engine.
  • FIG. 3 is a detailed drawing of the piston 13 .
  • the combustion chamber 14 is formed a dish-shaped recess.
  • the inner diameter of the combustion chamber 14 is a maximum at the inlet, the inner diameter being no greater at any point from the inlet towards the bottom.
  • the combustion chamber 14 is situated so that its center is effectively coaxial with the piston.
  • FIG. 11 shows a combustion chamber having a shape wherein the inner diameter is greater towards the bottom than at the inlet.
  • a turbulence B
  • a turbulence B
  • An inner diameter (d) of the inlet of the combustion chamber 14 has a size equal to or greater than 50 % of an outer diameter (D) of the piston 13 , i.e., d>0.5 ⁇ D.
  • FIG. 4 is a flowchart showing the details of the processing performed by a microprocessor in the controller 20 . This processing is repeated at a predetermined interval.
  • output signals are read from the engine rotation speed sensor 24 , accelerator opening sensor 25 , cooling water temperature sensor 26 and intake air temperature sensor 27 .
  • a step 2 the fuel injection amount and exhaust gas recirculation amount are set corresponding to running conditions at that time based on the signals read in the step 1.
  • a step 3 it is determined whether or not the engine is in an idle running state based on the running conditions signals read in the step 1. For example, if the output signal from the accelerator opening sensor 25 is a value showing the accelerator is fully closed and the output signal of the engine rotation speed sensor 24 is a value equal to or less than a predetermined rotation speed, it is determined that the engine is in the idle running state, and in other cases it is determined that the engine is in the normal running state.
  • step 3 If it is determined in the step 3 that the engine is in the idle running state, the routine proceeds to a step 4, and a pilot injection timing and main injection timing are set to perform two fuel injections.
  • the pilot injection timing is set in the vicinity of 30 degrees before compression top dead center
  • the main injection timing is set in the vicinity of 10 degrees before compression top dead center.
  • the opening of the throttle valve 3 is set to almost fully closed so as to reduce the intake air amount.
  • step 6 when it is determined in the aforesaid step 3 that the engine is in the normal running state, the routine proceeds to a step 6, and only the main injection timing is set to perform one fuel injection. According to this embodiment, this fuel injection timing is set to a timing which is delayed after compression top dead center.
  • the opening of the throttle valve 3 is set to fully open.
  • the controller 20 sends a negative pressure control signal corresponding to an exhaust gas recirculation amount set in the step 2 to the negative pressure regulating valve 9 .
  • a control signal corresponding to the opening of the throttle valve 3 set in the step 5 or the step 7 is also sent to the actuator 6 .
  • the fuel injection amount set in the step 2 is divided into a pilot injection amount and a main injection amount.
  • a fuel injection signal corresponding to the pilot injection amount is sent to the injector 16
  • a fuel injection signal corresponding to the main injection amount is sent to the injector 16 .
  • a fuel injection signal corresponding to the fuel injection amount set in the step 2 is sent to the injector 16 .
  • this adverse effect on combustion is resolved by performing two fuel injections, i.e., by performing a pilot injection before the main injection, when the opening of the throttle valve 3 is reduced to decrease the intake air amount.
  • the fuel injected in the pilot injection is ignited first, and the fuel injected in the following main injection therefore burns stably.
  • the distance from the injector 16 situated immediately above the combustion chamber 14 to the inner wall of the combustion chamber 14 is made longer by arranging that the inner diameter d of the combustion chamber 14 is equal to at least 50 percent of the outer diameter of the piston 13 .
  • the fuel injected from the injector 16 therefore forms a mist which expands conically around the nozzle of the injector 16 as center.
  • the fuel injected from the injector 16 is atomized before it reaches the inner wall, and the amount of fuel adhering to the inner wall decreases. This has the effect of suppressing generation of unburnt HC.
  • the injection of fuel in two stages is effective in improving ignitability and combustion stability by distributing more fuel near the center of the combustion chamber 14 , and as the amount of fuel in one injection is also reduced, less fuel reaches the inner wall of the combustion chamber 14 which also contributes to suppressing the generation of unburnt HC.
  • combustion chamber has a shape designed to reduce gas flow turbulence inside the combustion chamber 14 , it is impossible to increase the fuel diffusion speed by a large amount.
  • the fuel is burnt by premixed combustion, which is a form of combustion wherein smoke is not easily generated even if the gas flow is weak.
  • the fuel injection timing is delayed after compression top dead center, so the fuel ignition delay period (time from when fuel injection starts to when combustion of the injected fuel starts) is largely prolonged. It is possible to inject the entire fuel amount during this ignition delay period, thus the entire injected fuel amount forms a combustible mixture by mixing with air during the interval before ignition, and then self-ignites and bums by flame propagation.
  • the smoke generation amount can be suppressed to a low level even in a combustion chamber having the shape of this embodiment.
  • Combustion which is mainly premixed combustion carries a risk of a sharp increase in the rate of pressure rise, however due to the fact that the piston 13 begins descending at the combustion start point and the oxygen concentration in the combustion chamber 14 is reduced by performing exhaust gas recirculation, the combustion proceeds fairly slowly, and noise or vibration are not produced.
  • FIG. 5 compares pressure waveforms in the cylinder during the idle running state when normal combustion is performed with a compression ratio of 21 in a prior art diesel engine, when a pilot injection is performed at this compression ratio, when a pilot injection is performed and the compression ratio is reduced to 14, when the intake air is additionally throttled in the diesel engine according to this invention is used.
  • the pressure waveform in an ordinary gasoline engine is also shown. Compared to 75 bar in a prior art diesel engine, the pressure is reduced to about 30 bar according to this invention which is not very different from the 20 bar of the gasoline engine.
  • FIG. 6 is a diagram comparing internal cylinder pressure, unburnt HC and combustion noise according to this invention and the prior art. It is seen that while the discharge amount of unburnt HC is suppressed to effectively the same level, combustion noise is largely reduced. It should be noted that this comparison example shows characteristics when a low compression ratio is set first, and other conditions are then added successively.
  • variable valve mechanism 41 instead of providing the throttle valve to reduce the actual compression ratio in the idle running state, a variable valve mechanism 41 is provided which can delay the close timing of the intake air valve.
  • the close timing of the intake air valve is delayed to the vicinity of 90 degrees after intake bottom dead center.
  • a type is adopted which can function by oil pressure.
  • the intake air valve 22 in each cylinder is driven by a piston 43 disposed coaxially with it, and when the oil pressure acts on the piston 43 , the intake air valve 22 is pushed down against a valve spring 44 and opens. When the oil pressure is released, the intake air valve 22 is pushed back by the valve spring 44 and closes.
  • a pair of oil pressure supply valves 45 and a pair of oil pressure discharge valves 46 are provided to control the oil pressure acting on the piston 43 , and the oil pressure stored in an accumulator 48 is supplied or released via a pump to a pair of main circuits 47 . From the pair of main circuits 47 , oil pressure is supplied to or released from the piston 43 of each cylinder by a pair of change-over valves 49 .
  • the open/close timing and open/close period of the intake air valve 22 can be freely controlled.
  • the close timing of the intake air valve 22 is delayed to the vicinity of 90 degrees after intake bottom dead center, as shown in FIG. 8 .
  • the intake air valve 22 opens in the vicinity of exhaust top dead center and closes as a position slightly beyond intake bottom dead center, but this closing position may be considerably delayed.
  • the maximum internal cylinder pressure is reduced to the same order as that of a gasoline engine, as shown in FIG. 9 . If the throttle valve is closed and the intake air amount is reduced as in the previous embodiment, pumping loss occurs as in the gasoline engine, and this leads to an impairment of fuel-cost performance. However, according to this embodiment, the intake air amount can be reduced without causing pumping loss.
  • the pilot injection is performed in two stages.
  • a first pilot injection is performed in the vicinity of 40 degrees before compression top dead center, and then a second pilot injection is performed in the vicinity of 20 degrees before compression top dead center, as shown in FIG. 10 .
  • the intake air valve close timing is set to the normal timing and only a main fuel injection is performed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
US09/591,425 1999-06-10 2000-06-09 Diesel engine Expired - Fee Related US6332447B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP11-163659 1999-06-10
JP11163659A JP2000352326A (ja) 1999-06-10 1999-06-10 ディーゼルエンジンの制御装置

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EP (1) EP1059431B1 (de)
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DE (1) DE60019849T2 (de)

Cited By (9)

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Publication number Priority date Publication date Assignee Title
US6612292B2 (en) * 2001-01-09 2003-09-02 Nissan Motor Co., Ltd. Fuel injection control for diesel engine
US20040007203A1 (en) * 2002-07-09 2004-01-15 Rasmussen Jason J. Method of utilizing multiple fuel injections to reduce engine emissions at idle
US20040118377A1 (en) * 2002-12-19 2004-06-24 Bloms Jason K. Fuel allocation at idle or light engine load
US20060067343A1 (en) * 2004-09-30 2006-03-30 Brother Kogyo Kabushiki Kaisha Address information display system and address information display program
US7201121B2 (en) * 2002-02-04 2007-04-10 Caterpillar Inc Combustion engine including fluidically-driven engine valve actuator
CN100453782C (zh) * 2004-11-16 2009-01-21 丰田自动车株式会社 内燃机的气门正时控制装置和方法
US20120004826A1 (en) * 2010-06-30 2012-01-05 Mazda Motor Corporation Diesel engine and method of controlling the diesel engine
US8215292B2 (en) 1996-07-17 2012-07-10 Bryant Clyde C Internal combustion engine and working cycle
US9234478B2 (en) 2010-05-11 2016-01-12 Mazda Motor Corporation Diesel engine for automobile, control device and control method

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JP4403620B2 (ja) * 2000-01-11 2010-01-27 マツダ株式会社 筒内噴射式ディーゼルエンジンの制御装置
JP2007040274A (ja) * 2005-08-05 2007-02-15 Toyota Motor Corp 圧縮着火内燃機関の燃料噴射制御システム
JP4396697B2 (ja) 2006-12-13 2010-01-13 トヨタ自動車株式会社 ディーゼルエンジン燃料噴射制御装置
US20080156293A1 (en) * 2006-12-29 2008-07-03 Yiqun Huang Method for operating a diesel engine in a homogeneous charge compression ignition combustion mode under idle and light-load operating conditions
JP4732505B2 (ja) 2008-04-23 2011-07-27 本田技研工業株式会社 燃料直噴エンジン
DE102013213333A1 (de) * 2013-07-08 2015-01-22 Volkswagen Aktiengesellschaft Verfahren zum Betrieb einer selbstzündenden Brennkraftmaschine und Brennkraftmaschine mit Selbstzündung

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DE60019849T2 (de) 2005-11-10
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JP2000352326A (ja) 2000-12-19
EP1059431B1 (de) 2005-05-04

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